EP3235074B1 - Crimping pliers - Google Patents

Description

The invention relates to a pressing tongs, in particular for pressing cable lugs or the like onto electrical conductors, with two pressing jaws which can be pivoted relative to one another, wherein in each pressing jaw a pressing die formed over a circumference with respect to an axis of rotation with a plurality of different pressing troughs is rotatably mounted.

Crimping pliers of the type in question are known, both as hand-operated and as motor-operated tools. These are used, for example, to attach cable lugs to electrical conductors. For this purpose, a particularly tubular workpiece is pressed between the two press jaws using, for example, hexagonal press troughs of the press dies. There is usually a different press profile for each cable cross-section, i.e. a different opening cross-section of the press troughs of both press dies is required. Corresponding adaptation of the press dies is carried out in known pliers by rotating them around their axis of rotation, the press troughs of both press dies having to be matched to one another in order to properly press the workpiece.

Such pressing tongs are, for example, from the DE 19 628 752 B4 known.

In view of the known prior art, the object of the invention is to further improve a pressing tongs of the type in question, in particular with regard to handling.

This object is achieved with the subject matter of claim 1, the focus being on the fact that the press dies are continuously coupled in terms of gear independently of a pivoting position of the press jaws.

Due to the gear coupling of the press dies, the rotary adjustment of a press die to shift a desired press die into the working position automatically results in a corresponding adjustment of the other press die. Both press dies are adjusted synchronously. The coupling gear is preferably designed in such a way that press troughs of both press dies, which always belong to one another, move into the respective working position when a press die is adjusted.

The gear-type coupling of the press dies is always independent of the swivel position of the press jaws, i.e. preferably both in the maximum press jaw open position and in the press jaw closed position, and moreover preferably also in any intermediate position between the open position and the closed position. The coupling of the press dies is not lost in the course of swiveling the press jaws. The assignment of press troughs associated with the intended pressing, which is preferably given via the coupling, is always retained, preferably until a change is emphasized as a result of the rotational displacement of a press die.

A step-up or step-down can be achieved via the gear coupling.

A die can be moved transversely to the axis of rotation by means of a gear wheel. Due to the transverse displacement, a positive locking of the press die can be canceled in the working position. Furthermore, a radial displacement of the press die with respect to the axis of rotation can go hand in hand with the rotational displacement of the press die for setting another press trough in the working position.

Thus, it can further be provided that a press die can be moved by means of a gear wheel from a first press position secured by a form fit to a second press position secured by a form fit.

A press die can be displaced transversely to its axis of rotation in order to move another press trough into a working position by means of a gear action against a force acting on the press die in a form-locked work position. The force that loads the press die into the positively locked working position can result from a spring acting directly or indirectly on the press die. This can be a conventional cylinder spring in the form of a compression or tension spring; alternatively, for example, a leg spring. In addition, the force can also result from a resilient element in the form of an elastically resilient plastic or the like.

The gear coupling can be provided by gears that are constantly engaged. A preferred arrangement of such gearwheels coaxial with the swivel axes of the press jaws enables constant coupling of the gearwheels independently of the press jaw pivot position.

There can also be a constant coupling in terms of transmission by direct or indirect connection of the pressing dies via a transmission belt, furthermore in particular via at least one elastic belt.

It is also proposed that the press die can be moved transversely to its axis of rotation in order to cancel the positive-locking position.

In the solutions known from the prior art, the press dies are displaced along their axis of rotation in order to cancel the positive-locking position, in order to be able to spend another press trough in the working position after this, in particular because the press die can then be displaced in rotation.

The proposed solution here provides for a radial movement of the press die with respect to the axis of rotation in order to cancel the positive locking position. This results in cheaper handling. The movement transverse to the axis of rotation to cancel the positive locking position can go hand in hand with the rotational displacement of the press die to adjust the press trough. The transverse displacement can be derived from the rotational displacement. The rotational displacement can force the press die to move laterally.

To enable the press die to be displaced transversely, a bolt or the like which receives the axis of rotation and carries the press die can be guided in an elongated hole.

A pressing trough of the pressing die is preferably formed by tooth-like projections which flank tooth-like projections in particular the pressing trough in the circumferential direction of the press die. Each projection can have an action surface which can be brought into engagement with a form-locking means in a working position of a press body on an outer side of the press trough, viewed in the direction radial to an axis of rotation, the action surface brought into engagement with the form-locking surface with respect to one or through the axes of rotation of the opposing press dies or parallel straight lines enclose an acute angle. This acute angle can be, for example, 5 to 45 degrees, further, for example, 15 to 30 degrees.

The contact surface of the tooth-like projection preferably interacts with a corresponding form-fitting surface of the form-fitting means that runs at the same acute angle. The form-fitting surface and the pressurizing surface can rest against one another in the form-fitting position, in particular lie flat against one another.

The interlocking means with the interlocking surface is preferably fixed and therefore not displaceably attached to the press jaw assigned to the press die.

The engaging surface of a pressing trough can belong to a pressing trough which is opposite the axis of rotation of the pressing die and which is in the working position. A quasi rearward form-fit support of the press die can thus be achieved in the area of the form-fit means. In the case of a press die which can be rotated for adjustment, a plurality of press troughs of different designs are provided distributed over the circumference and are spaced apart from one another in the circumferential direction by tooth-like projections.

With respect to the straight line described above, two opposing application surfaces can be provided. These loading surfaces are preferably formed on the projections delimiting the pressing trough in the circumferential direction, wherein the loading surfaces can be arranged so as to point away from one another with respect to the straight line.

In the case of the formation of two opposing loading surfaces, two form-fitting surfaces interacting with these loading surfaces are preferably also provided.

The acute angles of both pressurizing surfaces and / or both positive locking surfaces can also be the same.

As a result of a preferred turning action on the press die, the action surface leading in the direction of rotation of the press die slides on the associated form-fitting surface of the form-fitting means. This leads to a displacement of the press die in a direction transverse to its axis of rotation until the loading surface leaves the form-fitting surface and the form-fitting engagement is thereby at least temporarily canceled.

The form-fitting surface on which the contact surface on the die side can slide can form a sliding surface, for example in the form of a guide slope, as a result of which the die can be brought into a stop-limited rotational end or form-fitting position when it is rotated about its axis of rotation. In particular in cooperation with a spring force acting on the die in its basic position, a possible unwanted remaining in the dead center position is counteracted. Rather, the die projection slides on the sliding surface that rises or falls with respect to a plan view, after which an automatic rotational displacement into the positive-locking position is achieved in particular by spring force.

With reference to a plan view, the sliding surface can have a curved edge edge course. The curve is calculated from the friction parameters of the press die and the form-fit surfaces of the form-fit agent, so that self-locking due to this friction pairing is impossible. The interacting surfaces of the press die and sliding surfaces meet at an angle (based on a plan view) that is preferably greater than 4 degrees.

Two oppositely directed guide bevels are preferably provided which, with reference to a top view of the dies and form-fit means, in which top view the die axes of rotation are represented as points, form a roof-like course of the form-fit surface.

In particular, if both pressurizing surfaces and form-fitting surfaces have the same angle, the above-described effect can be brought about in both directions of rotation of the press die. By changing the acute angle of one of the two contact surfaces and / or one of the two form-fitting surfaces, in particular towards an acute angle, further up to a parallel alignment to the straight line, an adjustment direction of rotation for the press die can be predetermined.

A press die can only be moved out of the positive-locking position against spring force for adjustment. At least this spring force has to be overcome to adjust the press die.

The spring force preferably acts transversely to the orientation of the axis of rotation of the press die on the press die or a bolt or the like guiding the press die. The spring acts in such a way that the press die is loaded directly or indirectly into the positive-locking position.

The spring force and / or the acute angle in the area of the contact surface and / or the form-fitting surface can be selected so that a direct manual adjustment of a press die is possible, i.e. in particular a translation-free rotational displacement of the press die due to a hand attack on the press die or an immediate actuator connected to the press die.

The spring force and / or the acute angle can also be selected such that only one gear adjustment is possible. In such a transmission adjustment, a gear ratio is preferably provided, so that larger spring forces and / or frictional forces between the loading surface and the form-fitting surface can also be overcome with the usual manual force.

A pressing tongs, in particular for pressing cable lugs or the like onto electrical conductors, with two pressing jaws which can be pivoted relative to one another, can have in each pressing jaw a pressing die rotatably mounted over a circumference with respect to an axis of rotation with several different pressing troughs formed thereon. Characters, in particular digits, can be provided which identify the different press troughs.

With regard to the characters, it is usually a matter of nominal press sizes of the assigned press troughs. In this regard, it is known to engrave these characters directly into the press matrices, for example in the area of tooth-like projections flanking the press troughs.

It can be provided that the characters are attached to a part separate from the press die, which is not subjected to a pressing force during pressing and consists of a material different from a material of the press die.

The usual engraving of the characters in the heavy-duty press dies proves to be complex. Often these characters are engraved by hand. The arrangement of the characters on a part separate from the die and not subjected to the pressing force during the pressing offers advantages in particular in the choice of the part material as well as in the choice of the application of the characters to the part. The Material can be chosen to be of less quality than the press die. For example, the part can consist of a common steel material, but can also consist, for example, of aluminum, plastic, cardboard or paper.

The characters can be printed on the separate part in the simplest way. The characters can also be stuck on, for example, as self-adhesive film.

The separate part can be firmly connected to the press die. For example, the separate part can be glued or screwed to the press die.

In one embodiment, the separate part can be arranged coaxially to the press die, for example in the case of a disk-like configuration of the separate part.

The separate part, with the characters belonging to the press mold in the working position, can visibly protrude over a free edge of the associated press jaw. A window-like cutout can also be provided, in particular in the area of the press jaw, through which the sign is visible.

In addition, the separate part can be arranged around a further axis of rotation separate from the axis of rotation of the press die and can be connected to the press die by means of a transmission. For example. the separate part can also be a handwheel for adjusting the press die.

If a permanent gear-type coupling is formed between the press dies, only a separate part with characters can be provided. Since the press dies are rotated synchronously into the working position and therefore always associated Press troughs facing each other in the working position, only one character display is necessary.

In addition to the printing of the characters on the separate part, an integral shaping of the characters with the separate part can also be provided, for example, according to punching into a separate part made of a metal material or further, for example, when the separate part is produced using the plastic injection molding process. In a preferred embodiment of the separate part as a zinc die-cast part, the characters can be incorporated at the same time in terms of casting technology.

Furthermore, the invention relates to pressing tongs according to the features of the preamble of claim 1.

In order to make such pressing tongs more economical, particularly in terms of handling technology, it is proposed that each pressing die be adjustable via an adjusting wheel coupled to it in a gearbox, the adjusting wheel and the pressing die having different axes of rotation.

Each press die can be adjusted via an associated setting wheel to move a press tray into the working position. The attack by the user, in particular by the user's hand, can take place at a distance from the press die. The setting wheel is connected to the press die by gears. There may be a direct effect of the setting wheel on the press die. An under- or translation can also be provided.

The setting wheel can have numbers, in particular numbers for marking the pressing trough in the working position.

The axes of rotation of the adjusting wheel and press die preferably run parallel to one another, in particular offset parallel to one another.

Each press jaw has an extension in the longitudinal direction, starting from a hinge of the press jaw on the associated handle to the free end assigned to the press die. The axes of rotation of the press die and setting wheel of a press jaw can be arranged offset to one another in this longitudinal direction.

The setting wheel can act directly on the pressing die, for example by designing the setting wheel and the pressing die or by forming sections of the same as friction wheels or gear wheels. A transmission-type coupling via a friction belt is also possible.

The setting wheel preferably acts on the press die via a gear wheel. The gear wheel is interposed in terms of transmission. Under- or translation can also be achieved here.

In addition, the die can be moved around a fixed, i.e. H. in particular, it cannot be rotatable transversely to the geometrical transverse axis.

The press die can also be secured in a press position by a form-fitting interaction with a spring. The found or set press die position is therefore preferably secured in a positive fit. For this purpose, a spring can be provided which interacts indirectly or, as is preferred, directly with the press die. The protruding radially to the axis of rotation of the die On the circumference, protrusions form loading surfaces, against which, in a preferred embodiment, the spring acts to form-fit interaction. A rotation of the press die from the press position is only possible by overcoming the spring force. By overcoming the spring force, the spring or a spring leg of the spring is deflected in particular by a projection of the press die.

The spring can be a wire spring, in particular a leg spring. In this regard, a leaf spring is preferred which, with a broad side in the pressing position, comes into contact with one or more contact surfaces of the pressing die on the projection side.

In a further embodiment, the leaf spring can be supported on the axis of a gear wheel. The leaf spring can also be bent about this axis of the gear wheel in order to apply the spring force. This bending area of the leaf spring is provided at least approximately in the middle of a longitudinal extension of the leaf spring. A free end area of the leaf spring acts against the press die. The other free end region of the leaf spring is preferably held in the region of the associated press jaw.

In the case of a pressing tongs of the type described at the outset, a gauge part can be provided which is adapted to an outer contour of the pressing die in the region of a pressing trough and only permits the pressing tongs to be closed if the pressing die is arranged in the pressing tongs with an alignment of a pressing trough suitable for pressing ,

Due to possible incorrect operation when adjusting the press die to use another press trough, it may happen that the press die does not reach its final, possibly locked position, but rather a slightly twisted position relative to it. This can cause damage during subsequent pressing of the press die. Such incorrect operation is counteracted by the proposed solution.

In the area of interaction with the press die or dies, the gauge part is adapted to the outer contour thereof, preferably outside the press troughs. If the press die is not correctly aligned, a protrusion extending in the circumferential direction between two press troughs blocks and / or guides against a flank of the gauge part in the course of the pliers closing movement.

If the press die is not correctly aligned, a flank of the gauge part can block the swivel path of a press die projection, so that the press position cannot be reached in this press die position.

The flank of the gauge part can also be aligned in such a way that positive control of the press die is achieved while the die projection runs along the flank, so as to shift at least one press trough adjacent to the projection into a working position.

The teaching part can be designed as a plate part. Thus, the teaching part in a floor plan, in which the geometrical axes of rotation of the press jaws are represented as points, can be triangular, with a triangular tip in the floor plan preferably being contour-matched to the facing outer contour of the projections that delimit the press troughs of both press dies on one side.

The material thickness viewed perpendicular to the surface extension of the plate part can correspond to the material thickness of a press die viewed in the same direction.

Furthermore, the teaching part preferably extends in a plane that also accommodates the two press dies.

Furthermore, the gauge part can be mounted on the swivel axes of the press jaws. So the gauge part can be penetrated by corresponding axle bolts. In the case of a possible triangular layout of the teaching part, these axes or axle bolts are preferably each assigned to a corner area.

The press dies, which are permanently coupled in terms of gearbox, regardless of a pivoting position of the press jaws, can be adjustable via a setting wheel, possibly with the interposition of a gear wheel, the gear wheel and / or the setting wheel being designed to be completely or partially elastically evasive.

As a result of this configuration, damage to the pressing tongs, in particular one or both pressing dies and / or components which are in operative position with this, is counteracted in the event of a possible misalignment of the pressing dies with respect to one another in the course of a pressing jaw closing movement. The forces acting on the press dies and / or on the gearwheel or gearwheels or the setting wheel do not lead to damage to the adjusting and / or pressing components due to the evasive design of the gearwheel and / or the setting wheel. Gear wheel and / or setting wheel, when there is a corresponding force effect, deflect entirely or in the form of a partial section essentially in the direction of force action due to a misalignment of the press dies. Gears can also be moved to a disengaged position or an overflow position. The preferred elasticity means that the gear wheel and / or setting wheel can be automatically returned to the original functional position when the force is removed.

The elastic evasibility can be given, for example, by a support of the gear wheel and / or adjusting wheel, which is essentially spring-loaded in the direction of force, and further, for example, an axle body of such a wheel. The gear wheel and / or setting wheel can also be made of an elastically yieldable material, such as rubber.

In addition, the gear wheel and / or the adjusting wheel can have toothed teeth, with which the gear wheel and / or adjusting wheel acts in the form of a toothed wheel, one or more groups of two or more toothed teeth being formed, the toothed teeth of one group being formed on a common mounting part and the mounting part is connected to a radially inner region of the gear wheel or setting wheel via a single springable branch.

A crimping tool can have a determination part for determining a diameter of an electrical conductor to be pressed onto, and the determination part can have a plurality of passage openings, each with a narrowest cross section, which corresponds to a nominal diameter of an electrical conductor.

It is thus possible to classify the conductor to be pressed in terms of the size and the press recess of the press dies to be selected thereafter. For this purpose, a teaching-like determination part can be provided. This can consist of a hard plastic, but alternatively also of a metal material. The passage opening, which corresponds to the conductor diameter, gives the user an indication of the press troughs to be set. For example, the determination part assigned to the passage openings can have corresponding markings, for example in the form of diameter designations or press trough designations.

The determination part can always be freely accessible for use on the pressing tongs. A fold-out arrangement of the determination part on the pressing tongs is preferred, so that the determination part can be pivoted from a position of use into a position of non-use when not in use. The non-use position can be a hidden position.

A relevant pivot axis of the determination part can be aligned parallel to the axes of rotation of the press dies.

The determination part can also be arranged in overlap with a jaw plate of a press jaw. As a result of pivoting, the determination part can be brought into the use position from this overlapping position.

Two jaw plates are preferably arranged to overlap one another, the determination part being able to be arranged between the jaw plates, in particular in the non-use position.

If one press jaw is equipped with an adjusting wheel for the synchronous adjustment of the press dies, the other press jaw can be provided with the swing-out determination part.

The passage openings of a determination part can be designed for customs-based cable sizes or also for those that are based on metrics.

In the case of a gearwheel with toothed teeth, wherein one or more groups of two or more toothed teeth can be formed and the toothed teeth of a group are formed on a common mounting part, the mounting part can be connected to a radially inner region of the gearwheel via a single resilient branch.

For this purpose it can be provided
that the branch is connected eccentrically to the holding part in the circumferential direction. As a result of this eccentric arrangement, in addition to resilient deflection in the circumferential direction, resilient deflection in the radial direction (with respect to the axis of rotation of the gear wheel) can also be achieved, even with a central loading, further particularly with a strictly radial loading on the mounting part.

The open-edged slots flanking the respective resilient branch extend over a radially greater length than the tooth gap that results in the circumferential direction between two toothed teeth.

Such a gearwheel can be produced using laser cutting technology. The resilient connection of a group of toothed teeth to the radially inner region enables elastic elasticity of this group of toothed teeth to be achieved with the corresponding application of force. The connecting branch acts like a feather leg.

The branch is preferably designed in the form of a circular segment with reference to a plan view of the gearwheel, thus at least approximately in the form of a leaf spring. The branch can also be connected eccentrically to the holding part in the circumferential direction, in particular in relation to an extension of the holding part in the circumferential direction of the gearwheel.

Three, four or more teeth are preferably formed on the mounting part. More preferably, there are several groups of four gear teeth on the gearwheel, more preferably eight groups.

The toothed teeth of all groups of a gearwheel result in a uniform, circumferential toothing along a circular line in the relaxed position of the branches carrying the holding parts.

The features described above are important both individually and in combination with one or more of the other features.

With regard to the disclosure, the ranges or ranges of values or multiple ranges specified above and below also include all intermediate values, in particular in 1/10 steps of the respective dimension, and therefore possibly also dimensionless. For example. The specification 5 to 45 degrees also includes the revelation of 5.1 to 45 degrees, 5 to 44.9 degrees, 5.1 to 44.9 degrees, 6.8 to 37.2 degrees etc. This disclosure can, on the one hand, serve as a limitation a specified range limit from below and / or above, alternatively or additionally, however, to disclose one or more singular values from a respectively specified range.

Figur 1:

In Ansicht eine handbetätigbare Presszange in einer ersten Ausführungsform, eine Pressbacken-Schließstellung betreffend;

Figur 2:

die Seitenansicht hierzu;

Figur 3:

den Schnitt gemäß der Linie III-III in Figur 2;

Figur 4:

die Vergrößerung des Bereiches IV in Figur 3;

Figur 5:

eine der Figur 3 entsprechende Darstellung, jedoch die Offenstellung der Pressbacken betreffend;

Figur 6:

eine der Figur 5 entsprechende Darstellung, mit in strichlinierter Wiedergabe von ineinander greifenden Zahnrädern;

Figur 7:

eine der Figur 6 entsprechende Darstellung, eine Zwischenstellung im Zuge der Verstellung der Pressmatrizen betreffend;

Figur 8:

in Ansicht eine Presszange in einer zweiten Ausführungsform;

Figur 9:

eine im Wesentlichen der Figur 3 entsprechende Darstellung, betreffend eine dritte Ausführungsform;

Figur 10:

eine weitere im Wesentlichen der Figur 3 entsprechende Darstellung, eine vierte Ausführungsform der Presszange als motorisch antreibbare Presszange betreffend;

Figur 11:

eine der Figur 3 entsprechende Darstellung, betreffend eine weitere Ausführungsform;

Figur 12:

in explosionsperspektivischer Darstellung eine Ausführungsform einer Pressmatrize mit koaxial zugeordnetem gesonderten Teil,

Figur 13:

eine der Figur 5 entsprechende Darstellung, eine weitere Ausführungsform einer Presszange betreffend;

Figur 14:

eine weitere Ausführungsform in einer Darstellung gemäß Figur 13;

Figur 15:

die Presszange gemäß Figur 14 in Pressstellung;

Figur 16:

eine der Figur 5 entsprechende Darstellung, jedoch eine alternative Ausführungsform hinsichtlich der Pressmatrizen betreffend;

Figur 17:

eine weitere Ausführungsform einer Presszange gemäß der Darstellung in Figur 5;

Figur 18:

die Presszange gemäß Figur 17 in Pressstellung;

Figur 19:

eine der Figur 17 im Wesentlichen entsprechende Darstellung, betreffend eine Fehlstellung der Pressmatrizen;

Figur 20:

eine der Figur 17 entsprechende Darstellung, eine alternative Ausführungsform betreffend;

Figur 21:

ein Formschlussmittel in Draufsicht, betreffend ein weiteres Ausführungsbeispiel;

Figur 22:

eine der Figur 6 im Wesentlichen entsprechende Darstellung, eine weitere alternative Ausführungsform betreffend;

Figur 23:

den Schnitt gemäß der Linie XXIII-XXIII in Figur 22;

Figur 24:

eine weitere der Figur 3 im Wesentlichen entsprechende Draufsicht auf eine Presszange, eine weitere Ausführungsform betreffend;

Figur 25:

ein Getrieberad der Presszange gemäß Figur 23 in Einzel-Draufsicht;

Figur 26:

die Herausvergrößerung des Bereiches XXV in Figur 24;

Figur 27:

in schematischer Darstellung ein Getrieberad in Anordnungsstellung, eine weitere Ausführungsform betreffend;

Figur 28:

eine der Figur 26 entsprechende Darstellung, betreffend eine weitere Ausführungsform;

Figur 29:

in perspektivischer Darstellung ein lehrenartiges Bestimmungsteil;

Figur 30:

die Draufsicht auf das Bestimmungsteil;

Figur 31:

den Schnitt gemäß der Linie XXX-XXX in Figur 29.

The invention is explained below with reference to the accompanying drawings, which, however, only represent exemplary embodiments. A part that is only explained with reference to one of the exemplary embodiments and in a further exemplary embodiment is not replaced by another part due to the particularity highlighted there, is therefore also described as a possible existing part for this further exemplary embodiment. The drawing shows:

Figure 1:

In view a hand-operated pressing tongs in a first embodiment, relating to a pressing jaw closed position;

Figure 2:

the side view of this;

Figure 3:

the section along the line III-III in Figure 2 ;

Figure 4:

the enlargement of area IV in Figure 3 ;

Figure 5:

one of the Figure 3 corresponding representation, but regarding the open position of the press jaws;

Figure 6:

one of the Figure 5 corresponding representation, with a dashed representation of intermeshing gears;

Figure 7:

one of the Figure 6 corresponding representation, regarding an intermediate position in the course of the adjustment of the press dies;

Figure 8:

in view a pressing tongs in a second embodiment;

Figure 9:

one essentially the Figure 3 corresponding representation, relating to a third embodiment;

Figure 10:

another essentially the Figure 3 corresponding representation, relating to a fourth embodiment of the pressing tongs as press tongs driven by a motor;

Figure 11:

one of the Figure 3 corresponding representation, regarding a further embodiment;

Figure 12:

an explosion perspective representation of an embodiment of a press die with coaxially assigned separate part,

Figure 13:

one of the Figure 5 corresponding representation, relating to a further embodiment of a pressing tongs;

Figure 14:

a further embodiment in a representation according to Figure 13 ;

Figure 15:

the pressing tongs according to Figure 14 in press position;

Figure 16:

one of the Figure 5 corresponding representation, but an alternative embodiment with regard to the press dies;

Figure 17:

a further embodiment of a pressing tongs as shown in Figure 5 ;

Figure 18:

the pressing tongs according to Figure 17 in press position;

Figure 19:

one of the Figure 17 essentially corresponding representation regarding a misalignment of the press dies;

Figure 20:

one of the Figure 17 corresponding representation, relating to an alternative embodiment;

Figure 21:

a positive locking means in plan view, relating to a further embodiment;

Figure 22:

one of the Figure 6 essentially corresponding representation, relating to a further alternative embodiment;

Figure 23:

the section along the line XXIII-XXIII in Figure 22 ;

Figure 24:

another of the Figure 3 essentially corresponding top view of a pressing tongs relating to a further embodiment;

Figure 25:

a gear wheel according to the pressing tongs Figure 23 in single top view;

Figure 26:

the enlargement of the area XXV in Figure 24 ;

Figure 27:

a schematic representation of a gear wheel in the arrangement position, relating to a further embodiment;

Figure 28:

one of the Figure 26 corresponding representation, regarding a further embodiment;

Figure 29:

in perspective a teaching-like determination part;

Figure 30:

the top view of the determination part;

Figure 31:

the cut along the line XXX-XXX in Figure 29 ,

Is shown and described initially with reference to Figure 1 a manually operable pressing tongs 1 in a plan view showing a working position, ie a pressing position. The pressing tongs 1 are constructed essentially symmetrically to an axis xx and have two pressing jaws 2, 3 and two handles 4, 5 designed as angle levers. The latter are connected at their angled ends by a pivot pin 6 arranged on the axis of symmetry xx.

On both sides of the hinge pin 6, the pressing jaws 2, 3 are articulated with their free end regions to the handles 4, 5, the pressing jaws 2, 3 and the handles 4, 5 passing through bolts 7, 8 which are secured with spring washers 9, 10 ,

The press jaws 2, 3, which are essentially identical in mirror image with respect to the axis xx, each consist first of two of the bolts in the axial direction 7, 8 and also the hinge pin 6 spaced-apart jaw plates 11, 12 and 13, 14. The bolt-side end regions of the handles 4, 5 engage in the space between the jaw plates 11, 12 and 13, 14, respectively.

The pressing jaws 2, 3 are connected both on the top and on the bottom, corresponding to the outward-facing flat side of the jaw plates, by tabs 15, 16, which in turn are interconnected by axis bolts 17, 18 passing through the pressing jaws 2, 3 are connected.

The geometric axes of the bolts 7, 8, the pivot pin 6 and the axle bolts 17, 18 are oriented transversely to the x-x axis and perpendicular to a plane extension of the pressing jaws 2, 3 with respect to their broad sides.

The axes of rotation of the pressing jaws 2, 3 are formed by the axle bolts 17, 18, whereby the pressing jaws 2, 3 are divided into short front lever arms 19, 20 and longer rear lever arms 21, 22 facing the joint bolts 7, 8.

In each of the front, short lever arms 19, 20 of the pressing jaws 2, 3, a pressing die 23, 24 is rotatably mounted on an axis 25, 26. The axes 25, 26 each pass through both jaw plates of the pressing jaws 2, 3 and are secured on both sides, for example by means of screwing. The geometric axis of rotation of the press dies is designated by y.

The press dies 23, 24 have the shape of an even polygon. In the embodiment shown, the press dies 23, 24 are designed as regular hexagons in plan.

The generally die-like press dies 23, 24 have press troughs 27, 28 with different opening cross sections on the circumference, each assigned to a side surface of the preferred hexagon.

In a top view, for example according to the Figure 3 the press troughs 27, 28 show the shape of a half equilateral hexagon. In working position, ie in the press position according to Figures 1 to 4 each form two press troughs 27, 28 with the same opening cross-section together to form a regular hexagon for pressing cable lugs, connectors or the like onto electrical conductors, etc.

For the correct pressing of a cable lug or the like, press troughs 27, 28 of the same size and adapted to the pressing must be brought into the working position. This is done by rotating the press dies 23, 24 about the axes 25, 26.

The rotational displacement of the press dies 23, 24 is synchronized. This is achieved by a constant gear coupling of the press dies 23, 24, which coupling is independent of the swivel position of the press jaws 2, 3.

For the transmission coupling is in a first embodiment according to the Figures 1 to 7 a gear wheel 29, 30 in the form of a gear wheel is rotatably arranged on each press jaw 2. The diameters of the gear wheels 29, 30 are the same.

Like the press dies 23, 24, the gear wheels 29, 30 extend in the space left between the jaw plates of the press jaws 2, 3.

The gear wheels 29, 30 are rotatably mounted on the axle bolts 17, 18, the gear wheel-shaped gear wheels 29, 30 meshing with one another. Due to the selected arrangement of the gear wheels 29, 30 on the axle bolts 17, 18, the meshing engagement with one another is ensured in every pivoting position of the pressing jaws 2, 3.

The outer diameter of each gear wheel 29, 30 corresponds approximately to the diameter of a circular line connecting the radial tips of the press dies 23, 24.

On the axles 25, 26, driven wheels 31, 32 are provided, which are non-rotatably connected to the respective pressing die 23, 24. With regard to the first embodiment, the driven wheels 31, 32 are gear wheels which mesh with the respectively assigned gear wheel 29, 39.

The diameter of the driven wheel 31, 32 is reduced compared to the diameter of the gear wheel 29, 30. An output wheel 31 thus has an outer diameter which corresponds approximately to 0.4 to 0.5 times the outer diameter of a gear wheel 29, 30.

Furthermore, the diameter of an driven wheel 31, 32 is selected such that, with reference to a projection along the axis of rotation y, it does not protrude into the press troughs 27 or 28 of the associated press die 23, 24.

Furthermore, a separate part 33 in the form of an adjusting wheel 68 is provided on a press jaw 3. This is rotatably mounted in the area of the rear, longer lever arm 22 about an axis bolt 34 with an axis of rotation z passing through the associated jaw plates 13, 14. The separate part 33 is designed with a circular disc a circular disk surface, which extends parallel to the wide surfaces of the gear wheels 29, 30 and the press dies 23, 24 offset from the plane.

Associated with a disk surface of the separate part 33, a drive wheel 35 in the form of a toothed wheel is provided on the latter in a rotationally fixed and coaxial manner. This meshes with the external toothing of the assigned gear wheel 30 of the press jaw 3.

The arrangement of the axle bolt 34 is preferably chosen so that the separate part 33 with a partial section over the outline contour of the press jaw 3 to the outside, i.e. facing away from the opposing press jaw 2, protruding freely, for operating the drive wheel 35 by hand. For example, the drive wheel 35 can be thumb-actuated by the thumb surface rotatingly displacing the separate part 33 over its peripheral edge.

A rotational displacement of the separate part 33 leads via the gearbox, consisting of drive wheel 35, gear wheels 29, 30 and driven wheels 31, 32, to a synchronous rotational displacement of the pressing dies 23, 24, so that only one part (separate part 33) is always the same by displacement Press troughs 27, 28 can be placed opposite each other in the working position.

As an alternative to the gear transmission arrangement, the transmission coupling according to the embodiment in FIG Figure 11 also be given by transmission belts.

The circular disk-shaped separate part 33 and the press dies 23, 24 in this case have non-rotatable and coaxially arranged cylinder sections 36 to 38, the outer surface of which can be roughened, for example, by microstructuring.

Such cylinder sections 39, 40 are also freely rotatably supported on the axle bolts 17, 18.

Each cylinder section 39, 40 on the axle pin side is connected to the cylinder section 36, 37 of the associated pressing die 23, 24 via an output belt 41, 42.

A drive belt 43, which may be laid crosswise, connects the cylinder section 40 on the axle bolt side to the cylinder section 38 of the separate part 33.

The two cylinder-bolt-side cylinder sections 39 and 40 are connected to one another via a transmission belt 44, which is preferably arranged in a cross.

On the separate part 33, signs 45 in the form of digits are applied to the circular disk surface thereof, which correspond to the nominal widths of the press troughs 27 and 28. The characters 45 are arranged on a circular line around the geometric axis of the axle bolt 34, such that the nominal size relating to the pressing troughs 27, 28 in the working position can be recognized by the user either on the section of the separate part 33 protruding beyond the outline of the pressing jaw 3 (see. Figure 1 or Figure 3 ) or through a window 46 punched out in the jaw plate 13 of the press jaw 3 covering the numerical side of the separate part 33 (cf. Figure 8 ).

Also, as in Figure 12 illustrated by way of example, a separate part 47 can be provided with, for example, printed 45 or integrally formed with the separate part characters 45, which part 47 is arranged coaxially with a press die 23, 24 and is further shaped, for example, in a contour-matched manner with the press die 23, 24 ,

The part 47 is non-rotatably connected to the pressing die 23, 24, for example by an out-of-round configuration of the bore through which the axis 25, 26 passes and the section of the axis which passes through.

Regardless of the design and arrangement of the separate part bearing the characters 45, this part is not subjected to any pressing force during pressing. In contrast to the press dies 23, 24, a different material is selected for the separate part, for example zinc die casting, which facilitates the application of the numbers 45, for example by printing or embedding the characters 45 in the course of the casting process.

The respective working position of the press dies 23, 24 is secured with a positive fit. For this purpose, a lug-like form-locking means 48, 49 is assigned to each pressing die 23, 24. The form-locking means 48, 49 extend in the space between the associated jaw plates of the pressing jaws 2, 3 and are held in the jaw plates by means of pin-like extensions 50, 51.

The form-locking means 48, 49 are arranged facing away from the press trough 27, 28 in the working position.

When viewed in the circumferential direction of each pressing die 23, 24, a tooth-like projection 52, 53, which is substantially radially oriented with respect to the geometric axis of rotation y of the pressing die 23, 24, extends between two adjacent pressing troughs.

Each projection 52, 53 has two contact surfaces 54, 55 and 56, 57, which form an obtuse angle with respect to one another in plan. The application surfaces result in a roof-shaped tapering of each projection 52, 53.

The application surfaces 54, 55 and 56, 57 extend further with respect to a plan according to Figure 3 on a line connecting the tips of the projections 52, 53 of a preferred hexagon contour.

The application surfaces 54, 55 and 56, 57 of the projections 52, 53, which limit the press recess 27, 28 located opposite in the working position, interact with adapted form-fitting surfaces 58 to 60 or 61 to 63 of the form-fitting means 48, 49.

The contact surfaces of the projections 52, 53 in the form-fitting position preferably bear against the associated form-fitting surfaces of the form-fitting means 48, 49.

With respect to a straight line A connecting the geometric axes of the axle bolts 17, 18, the form-fitting surfaces 59, 62 extend in the pressing position of the pressing jaws 2, 3 as shown in FIG Figure 4 in the transverse direction to the straight line A. The pressing recess facing the form-locking means 48, 49 27, 28 in the circumferential direction of the pressurizing surfaces 55, 57 of the pressing dies 23, 24 are supported in the form-fitting position on these form-fitting surfaces 59, 62, which are oriented transversely to the straight line A.

In the form-fitting position, the further application surfaces 54, 56 extend at an acute angle α of approximately 30 degrees to the straight line A (with reference to the pressing position according to FIG Figure 4 ).

The corresponding interlocking surfaces 58, 60 and 61, 63, starting from the interlocking surfaces 59, 62, run at a corresponding acute angle for the preferred full-surface contact of the corresponding contact surfaces.

The press dies 23, 24 are in the positive-locking position as shown in FIG Figure 3 secured against rotation. To rotate the press dies 23, 24, the positive connection must first be released. This takes place in conjunction with the rotating action on the pressing die 23, 24, in particular by the geared action by means of the separate part 33 by hand.

The axes 25, 26 of the press dies 23, 24 are guided in elongated holes 64, 65 of the press jaws 2, 3, which are aligned transversely to the alignment of the interlocking surfaces 59, 62 with respect to a floor plan. As a result, the press dies 23, 24 are transverse to the release of the positive locking the form-locking means 48, 49 relocatable.

Such a displacement takes place against the force of a spring 66. This can be a cylinder pressure spring, such as in Figure 1 shown to be in a radial bore the axis 25, 26 is seated against a boundary wall of the associated elongated hole 64, 65.

The spring can also be as shown in Figure 9 be a leg spring which is held in the area of the axle bolts 17, 18 and which acts with its free ends on the axes 25, 26 of the pressing die 23, 24 in the direction of the form-locking means 48, 49.

The spring force always acts in the direction of the positive locking position, regardless of the swivel position of the press jaws 2, 3.

To adjust the press dies 23, 24, the disc-shaped separate part 33 is shown in FIG Figure 6 preferably rotated in the direction of arrow a - with reference to the representation in the clockwise direction. This leads to an opposite rotation of the two gear wheels 29, 30 in the arrow directions b, c.

Via the gear wheels 29, 30, the driven wheels 31, 32 and correspondingly the pressing dies 23, 24 are rotatably displaced in the opposite direction d, e, which results in the positively guided transverse displacement of the pressing dies 23 by sliding the loading surfaces 54 and 56 on the associated form-fitting surfaces 60, 63 , 24 leads. This transverse displacement is superimposed by the rotational displacement of the die 23, 24.

If the projection 52, 53 following in the direction of rotation exceeds a dead center position (shown in FIG Figure 7 ) causes the spring force acting on the axes 25, 26 of the press dies 23, 24 a return of the press dies 23, 24 in the direction of the form-fitting position with the form-fitting means 48, 49.

As in the embodiment of the Figure 21 shown, the relevant interlocking surface 59 and 62 can be provided with two roof-like sliding surfaces 77. The form-fitting surface 59, 62 is thus preferably pointed at the level of a line connecting the die rotation axes y in the direction of the die 23, 24. The sliding surfaces 77 are designed to be adapted to a curve section with reference to a plan view, so that starting from one end, a positive-locking surface 59, 62 results first of all with a rising and then a falling surface.

When the dead center position is exceeded or reached, the pressing die 23, 24 experiences an angular momentum in the direction of the next positive locking position or before reaching the dead center position (if the turning force acting on the die ceases to exist) due to the spring force acting on it. Angular momentum in the direction of the previous positive locking position. An undesired remaining of the press die 23, 24 in the dead center position and self-locking is thus counteracted.

The press trough 27, 28, which is now in the working position, can be read in terms of its nominal size on the separate part 33.

If the application surfaces 54, 56 and the associated form-fitting surfaces 58, 60 and 61, 63 have the same acute angle to the straight line A, then a change of the pressing troughs 27, 28 can be achieved by turning the separate part 33 into one or the other Direction, in arrow direction a or opposite.

It is also possible for only one direction of rotation to be predetermined, in that one of the above-described angles of the contact surfaces and positive-locking surfaces has a comparatively small acute angle and thus form a stop which cannot be overflowed.

Adjustment of the press dies 23, 24 when the press jaws 2, 3 are open can also be carried out by directly grasping one of the press dies 23 or 24 (this may be done with the disc-shaped separate part 33 omitted). The movement of the one press die 23 leads to the synchronous movement of the other press die via the gear provided.

In Figure 10 An electrically actuated pressing tongs 1 is shown, in which the pressing jaws 2, 3 are moved into the pressing position and back by means of a plunger which can be actuated by an electric motor. The pressing process is triggered by a lever 67 that can be actuated by a finger.

The pressing tongs as shown in Figure 10 has a transmission as described above for coupling the press dies 23, 24, and a disk-shaped separate part 33 for manual adjustment of the press dies. Numbers 45 are plotted on the separate part 33 or embedded in the part to indicate the set nominal width of the press troughs 27, 28.

The mode of operation with respect to the adjustment of the pressing dies 23, 24 is the same as that of the manually operated pressing tongs 1.

In Figure 13 shows a further embodiment of a pressing tongs 1, in which an adjusting wheel 68, 69 is arranged on each pressing jaw 2, 3. Here too the Axis of rotation z of each setting wheel 68, 69 is arranged parallel and offset in the longitudinal direction of the pressing jaw 2, 3 to the axis of rotation y of the associated pressing die 23, 24.

The setting wheels 68, 69 are coupled via gear wheels 29, 30 to the associated pressing die 23, 24 in terms of transmission.

In this embodiment, the gear wheels 29, 30 are arranged such that their toothed rings do not mesh with one another in any swivel position of the pressing jaws 2, 3.

In this embodiment, an adjusted press jaw is adjusted by individually adjusting both press dies 23, 24 via the respective setting wheel 68, 69.

The press dies 23, 24 are also adjusted here by attacking an area spaced apart from the press dies 23, 24, in particular as a result of the rotational displacement of the associated setting wheel 68, 69.

This also offers the advantageous possibility of placing the press jaw numbers 45 on the setting wheels 68, 69.

The Figures 14 and 15 show an embodiment with a synchronous adjustment of the press dies 23, 24, for example according to the first embodiment.

One of the press jaws, here the press jaw 2, carries a pawl 70 which is rotatably mounted about a parallel to the pivot axis of the press jaw 2 the compression jaw 2 other ends of the tension spring 71 in a basic position according to Figure 14 loaded.

The pawl 70 has a pawl nose 72. This points in the basic orientation Figure 14 in the direction of the articulation point of the handle 4 on the press jaw penetrated by the bolt 7.

A radial boom is also formed on the pawl 70. This nose 73 pointing laterally towards the other press jaw 3 serves as an emergency release.

In the area of the articulation point of the handle 4 penetrated by the pin 7, a gearwheel segment 74 is formed coaxially with the pin 7 or with the pin axis thereof, for interaction with the pawl nose 72.

The pawl 70 is arranged lying between the jaw plates 11, 12 of the pressing jaw 2 and engages in an open position of the pressing tongs 1 according to Figure 14 in a non-toothed area of the articulation point.

When the handles 4 and 5 are pivoted to close the pressing tongs 1, the pawl nose 72 engages in the gearwheel segment 74, so that from this position alone a further displacement of the handle 4 in the direction of the other handle 5 can be carried out.

Such a forced lock ensures that the full pressure must always be exerted when establishing a press connection.

When the pressing position is reached, the pawl nose 72 has overflowed the gear segment 74 and is then again in its extended starting position (cf. Figure 15 ) so that the ratchet-like overflow enables the handles 4, 5 to be opened or the pressing tongs 1 to be opened.

In an emergency, the pawl 70 can be shifted into a non-engaged position by the user via the nose 73, so that the pressing tongs 1 can also be opened without completing a pressing operation.

Figure 16 shows an alternative embodiment with press matrices 23, 24, each drawing a regular pentagon with respect to the floor plan with respect to its outer contour.

Correspondingly, five press troughs 27, 28 are provided over the circumference, centrally assigned to the longitudinal edge edges. The projections 52, 53 extend between them in the circumferential direction.

The projection 52, 53 diametrically opposite the press trough 27, 28 in the working position, in cooperation with the form-locking means 48, 49, serves to secure the press die 23, 24 in the working position.

For this purpose, the protrusion 52, 53 dips with its tip region having the action surfaces 54 and 56 into a notch-like depression of the form-locking means 48, 49, which notch-like depression form the corresponding form-locking surfaces 58, 60 and 61, 63, respectively.

The interlocking surfaces 58, 60 and 61, 63 extend with respect to the plan according to Figure 16 beyond the press trough 27, 28 adjacent to the captured projection 52, 53. It is further preferred that the application surfaces of the projection 52, 53 leading or trailing in the direction of rotation of the press die 23, 24 are supported.

In the embodiment according to the Figures 17 to 19 is based on a pressing tongs as shown in the Figures 1 to 6 , a teaching part 75 is provided. This is preferably a plate part with an essentially triangular plan as shown in FIG Figure 17 ,

The gauge part 75 preferably extends between the jaw plates, so correspondingly preferably in the plane of the press dies 23 and 24. The gauge part 75 can have a thickness considered in the axial direction of the press dies 23 and 24, which corresponds to that of the press dies 23, 24.

Furthermore, the gauge part 75 in the embodiment shown is penetrated by the axle bolts 17 and 18 in the region of two triangular tips and is thus held.

The result is a triangular tip 76 of the gauge part 75, which tip protrudes into the mouth of the pressing tongs 1, into which mouth the pressing troughs 27, 28 also protrude when the pressing dies 23 and 24 are properly aligned.

The flanks of the tips 76 are adapted to the outer contour of the projections 52 and 53, in particular adapted to the contact surfaces 55 and 57.

The pressurizing surfaces 55, 57 of two projections 52, 53 which face each other in the working position close in the pressed position according to Figure 18 an obtuse angle of, for example, 120 degrees, which corresponds to the included angle of the pointed flanks of the gauge part 75.

If the press dies 23 and 24 are correctly and securely locked as shown in Figure 17 press jaws 2 and 3 can be closed. The application surfaces 55, 57 of the projections 52 and 53, which are in the pressing position and essentially face each other, are supported, if necessary, on the pointed flanks of the gauge part 75.

If, on the other hand, the press dies 23 and 24 are not completely shifted in their final and preferably locked position (cf. Figure 19 ) at least one of the projections 52, 53 hits against the facing flank of the gauge part tip 76 in the course of the pliers closing movement. This can result in the pliers closing movement being prevented, according to locking.

The flanks of the teaching part 75 adjoining the tip region are preferably concave when viewed from the teaching part 75 to the outside. This provides a controlled guidance of the projection 53, 53 which strikes the press die in the course of the pincer closing movement, preferably in the direction of the usual rotational displacement direction of the press die 23, 24 until the working position is reached.

Figure 20 shows an embodiment with a gauge part 75 of the type described above, in which pressing tongs 1 the pressing dies 23 and 24 are individually and directly adjustable by hand.

The Figures 22 and 23 show a further embodiment of a pressing tongs 1 with pressing dies 23 and 24 which can be adjusted synchronously via gear wheels 29 and 30 and preferably an adjusting wheel 68.

In this embodiment, the press dies 23 and 24 are rotatably supported about fixed axes 25 and 26, which preferably cannot be displaced transversely to the axis y.

A pressing position of the pressing dies 23, 24 found in particular via the setting wheel 68 and the gear wheels 29, 30 is also ensured in this embodiment. For this purpose, each press die 23, 24 is assigned a spring 78 in the form of a leaf spring. The spring 78 is fixed in the region of one end to a mounting pin 79, which mounting pin 79 is held on the associated press jaw 2, 3, in particular between the associated jaw plates. The spring 78 extends from the mounting pin 79 in the direction of the associated pressing die 23, 24, in this case partially surrounding the axle bolt 17, 18 with resilient bending of the associated gear wheel 29, 30, so that the spring 78 is supported with one of its broad sides the axle pin is reached.

The end of the spring 78 facing away from the end of the bracket extends after the support area on the axle bolt 17, 18 in a direction facing away from the press trough 27, 28 in the press position.

The spring 78 is supported with its free area stretched over the axle bolts 17, 18 on the facing application surfaces 55 and 57 of two successive projections 52, 53 in the direction of rotation of the pressing die 23, 24. Due to the spring force acting on the projections 52, 53, there is a positive locking interaction for securing the press die 23, 24 in the press position found reached. The press die 23, 24 is inevitably rotated against the (in relation to the illustration in FIG Figure 22 ) counter-clockwise force of the spring 78. By rotating the die 23, 24, the free spring leg is further deflected.

The width of the leaf spring viewed in the direction of the axis of rotation y of the pressing die 23, 24 preferably corresponds to the height, viewed in the same direction, of the contact surfaces interacting with the spring 78 and thus more preferably to the material thickness of the pressing die 23, 24 in the region of the projections, viewed further in the axial direction 52, 53.

Figure 24 shows a further embodiment of the pressing tongs 1. In this, too, the pressing dies 23, 24 can be adjusted jointly and synchronously via gear wheels 29, 30, for which purpose an adjusting wheel 68 acting on a gear wheel is further provided.

The gear wheels 29, 30 are of identical design.

Furthermore, the gear wheels 29, 30 are designed to be elastically evasive. For this purpose, the tooth teeth 80 of each gear wheel 29, 30 are divided into groups 81 of four tooth teeth 80 which follow one another in the circumferential direction.

The tooth teeth 80 of a group 81 are formed on a holding part 82. A resilient branch 83, which is connected to a radially inner area 84 of the gear wheel 29, 30, which is also of the same material and in one piece, continues from the same material and in one piece.

The gear wheel 29, 30 or gear 86 has eight groups, each with four toothed teeth 80, distributed uniformly over the circumference, which eight groups 81 are each connected to the inner region 84 via a branch 83.

The branches 83 are connected eccentrically to the holding part 82 with respect to a radial r (with respect to the geometric axis of rotation of the gear wheel 29, 30 or the gear 86), which radial r passes through the holding part 82 in its circumferential extent. The connection of the branch 83 in the circumferential direction is preferably formed at the end of the holding part 82.

In each case one toothing tooth 80 can form the end region of the holding part 82. The radial r can run centrally through a tooth gap formed between the central toothing teeth 80.

Starting from the connection to the holding part 82, each branch 83 runs according to FIG Figure 24 Curved section-shaped, in this case proceeding from the holding part 82 away from it in the circumferential direction and engaging radially on the inside adjacent group 81 or the holding part 82.

The connection of the branch 83 to the radially inner region 84 can be selected such that a radial penetrating this connection region in the middle at least approximately intersects the branch connection region on the holding part 82 of the group 81 adjacent in the circumferential direction.

Due to the above-described configuration of the gear wheel 29, 30 or gear wheel 86, a resilient evasibility of an engaged group 81 of Gearing teeth 80 are given, even with a central, in particular strictly radial, action, wherein a resilient effect can be achieved both in the radial and in the circumferential direction.

Alternatively, a resilient effect can also be achieved by forming the gearwheel 86, for example the gearwheel 29, 30, from a resilient material, and further, for example, by forming the same from a rubber material. A resilient displacement as exemplarily and schematically in FIG Figure 27 shown to be provided. For example, the axle pin 17, 18 can be guided in an elongated hole in a jaw plate and can be loaded into a central working position by compression springs 88.

Alternatively, the gearwheel 86, such as the gearwheel 29, 30, but also the setting wheel 68, 69, can be formed by a circumferential ring gear 89 which is connected to the inner region 84 via resilient spring arms 90 which run in a circular section in plan view is (cf. Figure 28 ).

In order to be able to classify the conductor to be pressed in terms of the press trough size, a gauge-like determination part 91 can be provided. This is plate-like shape, for example consisting of a hard plastic, alternatively of a metal material.

The determination part 91 can be pivotably arranged on the pressing tongs 1, in particular between the jaw plates 11, 12.

The determination part 91 can have integral pivot pins 92 which are seated in corresponding bores or depressions in the jaw plates 11, 12. The the resulting geometric axis of rotation runs parallel to the axes y of the press dies 23, 24.

The determination part 91 is thus from a non-use position, in which it is arranged between the overlapping jaw plates 11, 12 in an in Figure 24 Folded out use position shown in dash-dotted lines.

In order to grip the determination part 91, a gripping section 93 is also formed which projects freely beyond the facing edge edges of the jaw plates 11, 12 even in the non-use position.

In addition, friction projections 94 can be provided on both broad side surfaces of the determination part 91 near the pivot 92, which hold the determination part 91 in the non-use position due to frictional engagement with the facing surfaces of the jaw plates 11, 12.

Furthermore, the determination part 91 has a plurality of passage openings 95 which pass through the broad side surfaces of the determination part 91. The number of passage openings 95 is preferably adapted to the number of pressing troughs 27, 28 of the pressing dies 23, 24.

Each passage opening 95 has a narrowest cross section, in particular in the region of an annular collar-like extension in the region of a broad side surface of the determination part 91, which narrowest cross section corresponds to a nominal diameter of an electrical conductor.

Associated with the passage openings 95, information on the pressing troughs 27, 28 can be provided on the broad side of the determination part 91, which corresponds to the setting information on the setting wheel 68 or directly on the pressing dies 23, 24. This enables the electrical conductor and thus the cable lug or the like to be crimped, as well as the crimping cavities 27, 28 to be set, to be clearly classified.

In order to facilitate the insertion of the electrical conductor into the passage opening 95, this has an insertion funnel-like section 96 at least on one side. This is preferably formed on the broad side of the determination part 91 opposite the annular collar. <B> LIST OF REFERENCES: </ b> 1 crimping pliers 31 output gear 61 Form-fit area 2 pressing jaw 32 output gear 62 Form-fit area 3 pressing jaw 33 part 63 Form-fit area 4 handle 34 axle 64 Long hole 5 handle 35 drive wheel 65 Long hole 6 pivot pin 36 cylinder section 66 feather 7 bolt 37 cylinder section 67 lever 8th bolt 38 cylinder section 68 dial 9 spring washer 39 cylinder section 69 dial 10 spring washer 40 cylinder section 70 pawl 11 Back plate 41 driven belts 71 mainspring 12 Back plate 42 driven belts 72 latching tab 13 Back plate 43 drive belts 73 nose 14 Back plate 44 transmission belt 74 gear segment 15 flap 45 character 75 teaching part 16 flap 46 window 76 top 17 axle 47 part 77 sliding surface 18 axle 48 Fit means 78 feather 19 lever arm 49 Fit means 79 support posts 20 lever arm 50 extension 80 teeth tooth 21 lever arm 51 extension 81 group 22 lever arm 52 head Start 82 supporting member 23 stamper 53 head Start 83 branch 24 stamper 54 actuating area 84 Inner area 25 axis 55 actuating area 85 slot 26 axis 56 actuating area 86 gear 27 Press depression 57 actuating area 87 Long hole 28 Press depression 58 Form-fit area 88 compression spring 29 Pinion 59 Form-fit area 89 sprocket 30 Pinion 60 Form-fit area 90 spring arm 91 determining part 92 pivot 93 cross section 94 Reibvorsprung 95 Port 96 section A Just α angle a arrow b arrow c arrow d arrow e arrow r radial x axis y axis z axis

Claims (15)

1. Crimping pliers (1), in particular for crimping cable lugs or the like onto electrical conductors, comprising two crimping jaws (2, 3) which can be swivelled towards one another, wherein in each crimping jaw (2, 3) a crimping matrix (23, 24) configured with a plurality of different crimping dies (27, 28) over a circumference is rotatably mounted with respect to an axis of rotation (y), characterized in that the crimping matrices (23, 24) are permanently coupled to each other via the gearing independently of a swivel position of the crimping jaws (2, 3).
2. The crimping pliers according to claim 1, characterized in that a crimping matrix (23, 24) is movable by means of a gear wheel (29, 30) transversely to the axis of rotation (y).
3. The crimping pliers according to any one of the preceding claims, characterized in that a crimping matrix (23, 24) is movable by means of a gear wheel (29, 30) from a first crimping position protected by interlocking into a second crimping position protected by interlocking.
4. The crimping pliers according to any one of the preceding claims, characterized in that a crimping matrix (23, 24) can be adjusted to move another crimping die (27, 28) into a working position by means of a gear action against a force urging the crimping matrix (23, 24) into an interlocked working position accompanied by a movement transverse to its axis of rotation (y).
5. The crimping pliers according to any one of the preceding claims, characterized in that, characterized in that each crimping matrix (23, 24) is adjustable by means of an adjusting wheel (68, 69) coupled to this via the gearing, wherein the adjusting wheel (68, 69) and the crimping matrix (23, 24) have different axes of rotation (y, z).
6. The crimping pliers according to claim 5, characterized in that the axes of rotation (y, z) run parallel to one another.
7. The crimping pliers according to one of claims 5 or 6, characterized in that a crimping jaw (2, 3) has a longitudinal direction from a hinge on the handle side to a free end, and that the axes of rotation (y, z) are offset with respect to one another in the longitudinal direction.
8. The crimping pliers according to one of claims 5 to 7, characterized in that the adjusting wheel (68, 69) acts on the crimping matrix (23, 24) via a gear wheel (29, 30).
9. The crimping pliers according to one of claims 5 to 8, characterized in that the crimping matrix (23, 24) is rotatable about a fixed axis (25, 26).
10. The crimping pliers according to one of claims 5 to 9, characterized in that the crimping matrix (23, 24) is secured in a crimping position by a positive interaction with a spring (78) wherein preferably the spring (78) is a leaf spring.
11. The crimping pliers according to claim 10, characterized in that the spring (78) is supported on the axis (17, 18) of a gear wheel.
12. The crimping pliers according to any one of the preceding claims, characterized in that one or both of the crimping matrices (23, 24) are adjustable by means of an adjusting wheel (68, 69) optionally with an interposed gear wheel (29, 30) and that a gear wheel (29, 30) and/or the adjusting wheel (68, 69) is formed completely or partially as elastically yieldable.
13. The crimping pliers according to claim 12, characterized in that the gear wheel (29, 30) and/or the adjusting wheel (68, 69) have teeth (80), wherein one or several groups (81) of two or more teeth (80) are formed, wherein further the teeth (80) of one group (81) are formed on a common retaining part (82) and the retaining part (82) is connected to a radially inner region (84) of the gear wheel (29, 30) or adjusting wheel (68, 69) via a single spring-loadable branch (83).
14. The crimping pliers according to claim 13, characterized in that the branch (83) is connected to the retaining part (82) off-centre in the circumferential direction.
15. The crimping pliers according to claim 13 or 14, characterized in that three, four or more teeth (80) are formed on the retaining part (82).

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